Mechanical seal assembly

ABSTRACT

A split mechanical composite seal assembly for providing a seal between a rotating shaft and a static surface. The split mechanical composite seal assembly includes first and second axially adjacent annular seal elements. The first and second seal elements each include a sealing edge contacting the shaft to provide a respective seal between the first and second seal element and the shaft. A static housing receives the first and second seal elements and engages the static surface to provide a static stationary seal, while concomitantly providing a flex region that engages the seal elements to form a dynamic seal therewith. A holder assembly receives one seal element and may include a double-angled lead-in to facilitate installation of the seal element. The holder assembly may include a detent groove for receiving and retaining an O-ring disposed about the seal element. The static housing may comprise two mating segments having overlapping surfaces.

FIELD OF THE INVENTION

The present invention relates to a seal assembly for sealing a shaft ora rod relative to a stationary housing component. This invention relatesgenerally to mechanical seals. More particularly, the present inventionrelates to universal split mechanical seals that provide strong sealingcapabilities under different operating conditions.

BACKGROUND OF THE INVENTION

Conventional mechanical seal assemblies are employed in a wide varietyof environments and settings, such as for example, in mechanicalapparatuses, to provide a fluid-tight seal. The sealing assemblies areusually positioned about a rotating shaft or rod that is mounted in andprotrudes from a stationary mechanical housing.

Split mechanical seals are employed in a wide variety of mechanicalapparatuses to provide a pressure-tight and fluid-tight seal. Themechanical seal is usually positioned about a rotating shaft that ismounted in and protruding from a stationary housing. The seal is usuallybolted to the housing at the shaft exit, thus preventing the loss ofpressurized process fluid from the housing. Conventional splitmechanical seals include face-type mechanical seals, which include apair of sealing rings that are concentrically disposed about the shaft,and axially spaced from each other. The sealing rings each have sealingfaces that are biased into sealing contact with each other. Usually, oneseal ring remains stationary, while the other ring contacts the shaftand rotates therewith. The mechanical seal prevents leakage of thepressurized process fluid to the external environment by biasing theseal ring sealing faces in sealing contact with each other. The rotaryseal ring is usually mounted in a holder assembly which is disposed in achamber formed by a gland assembly. The holder assembly may have a pairof holder halves secured together by a screw. Likewise, the glandassembly may have a pair of gland halves also secured together by ascrew. The sealing rings are often divided into segments, each segmenthaving a pair of sealing faces, thereby resulting in each ring being asplit ring that can be mounted about the shaft without the necessity offreeing one end of the shaft ends.

Prior split mechanical seals have rotary and stationary componentsassembled around the shaft and then bolted on to the equipment to besealed. A rotary seal face is inserted into a rotary metal clamp afterthe segments are assembled around the shaft. Then, the stationary facesegments and gland segments are assembled and the split gland assemblyis then bolted to the pump housing.

Previous split mechanical seal designs posed several problems. A firstproblem with prior split mechanical seal designs relates to theinsertion of the rotary seal ring into the holder assembly that isclamped around the shaft. An O-ring seals the rotary seal face to theclamped holder in an axial direction. The rotary seal face must bepushed into a tight space inside the clamped holder, and some difficultymay often be encountered. The elastomeric O-ring sealing the rotary sealface to the holder needs to be compressed for sealing, and a certainamount of force is required to insert the seal face inside the clampedholder. In addition, since the O-ring tends to grab the seal ring andinhibits sliding, the rotary seal face of prior art mechanical sealassembly designs has a tendency to “pop-out” after being inserted.Further, the movement of the O-ring when installed can result in theO-ring being disposed in an angled position, rather than a morepreferred vertical position relative to the rotary seal ring. From theangled position, the installer would be required to move the O-ring backto the original position, which is difficult. This process can requireseveral attempts during installation to have the rotary seal faceproperly seated inside the clamped holder.

Another important consideration is to maintain perpendicularity of therotary seal face to the shaft for smooth operation. It is quite possibleto have one side of the rotary seal face further inside the clampedholder than the other side. The result is an out-of-squareness conditionof the rotary seal face with respect to the shaft axis. This in turncreates a back and forth motion of the stationary seal ring as it tiltsfrom side to side in order to track the rotary seal ring with everyshaft revolution. If significant enough, this can result in shortenedseal life.

Another problem experienced with prior split mechanical seal designsoccurs when excessive torque is applied to the gland bolts whiletightening the seal gland to the pump or other equipment housing. Thisproblem is most severe when only two gland bolts are used. Since two andfour bolt configurations are the most common bolt designs, bolt slotsare typically not provided in an even symmetrical location with respectto the gland splits. Indeed, when two bolts are used the most logicalbolt location would be to have them located 90 degrees from the split.If this were done, however, when four bolts are used, the other twobolts would be located right at the split, which is undesirable. Toavoid this design occurrence, the slots are located anywhere from about15 to 45 degrees from the split line.

Therefore when only two bolts are used for the gland assembly, theloading on the gland halves is not symmetrical or even with respect tothe split plane. The face gasket which is compressed between the glandand the housing is typically of an elastomeric material which isresilient enough to provide a seal. Given the uneven nature of theclamping load, the bolting force must be transmitted on each side of thesplit by the joining mechanism of the gland halves. These are typicallyan alignment pin and a securing screw tangential to the shaft outerdiameter (compared to the axial direction of the gland bolts). Thealignment pins are quite small in relation to the forces applied, andtherefore cannot ensure that the gland halves will not slide againsteach other thereby distorting the alignment pin and the gland halves.The result is twofold: first there is a reduction in sealing ability ofthe gaskets between the gland halves, and second, there is anout-of-round twisting of the gland assembly which creates sealingproblems with the stationary seal ring.

SUMMARY OF THE INVENTION

The present invention provides an improved mechanical seal assembly forsealing a component, such as a pump or any rotating equipment. Themechanical seal assembly may include a rotary seal ring connected tomoving components of the equipment being sealed, a stationary seal ringthat creates a seal against the rotary seal ring and is connected tostationary components of the equipment being sealed, and associatedassembly components. The improved mechanical seal assembly may include arotary seal ring holder clamped around the shaft for holding the rotaryseal ring in a selected position and configuration. The rotary seal ringholder is configured to facilitate installation of the rotary seal ringinto the rotary seal ring holder and maintain the perpendicularity ofthe rotary seal face to the shaft being sealed. The rotary seal ring mayinclude a detent for capturing and aligning a sealing element, such asan O-ring, for sealing against a radially outer surface of the rotaryseal ring. A double angled lead-in facilitates insertion of the rotaryseal ring and O-ring into the rotary seal ring holder.

The improved mechanical seal assembly may include a gland assemblyhaving interacting, mating halves to facilitate engagement of the glandhalves and reduce or prevent sliding of the gland halves relative toeach other when forces from the bolts, the equipment housing, the gasketsupport and/or other sources are applied to the gland assembly.

According to a first aspect of the invention, a gland assembly for asplit mechanical seal assembly for providing a seal around a shaft, theshaft extending along a longitudinal axis from stationary equipment ifprovided. The gland assembly comprises a first arcuate gland segmenthaving a first interfacing surface formed at a first end a secondinterfacing surface formed at a second end and a second arcuate glandsegment having a third interfacing surface formed at a first endconfigured to couple to the first interfacing surface and a fourthinterfacing surface at a second end configured to couple to the secondinterfacing surface to form an annular gland assembly. At least one pairof the coupled interfacing surfaces are non-flat and shapedcomplimentary to each other to transmit a bolting force to the othermating gland segment.

According to another aspect of the invention, a split mechanical sealassembly is provided, which comprises a pair of stationary glandsegments defining a chamber and having an inner face, each gland segmenthaving at least one interfacing surface configured to interface with andoverlap a corresponding interfacing surface of the other gland segment,a pair of rotating holder segments disposed within said chamber andradially spaced from said gland segments, a stationary seal ringassembly disposed within said chamber and axially spaced from saidholder segments, and a rotating seal ring assembly disposed within saidrotating holder and axially spaced from and in intimate contact withsaid stationary seal ring.

According to still another aspect of the invention, a method ofassembling a gland for a split mechanical seal assembly is provided. Themethod comprises the steps of providing a first arcuate gland segmenthaving a first interfacing surface formed at a first end a secondinterfacing surface formed at a second end, wherein the firstinterfacing surface is non-flat, and providing a second arcuate glandsegment having a third interfacing surface formed at a first endconfigured to couple to the first interfacing surface and a fourthinterfacing surface at a second end, wherein the third interfacingsurface is non-flat and shaped complimentary to the first interfacingsurface. The method further comprises the step of coupling the firstinterfacing surface and the third interfacing surface, and the secondinterfacing surface to the fourth interfacing surface to form an annulargland assembly, such that a portion of the first interfacing surfaceoverlaps a portion of the second interfacing surface to transmit abolting force to from one segment to the other.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other features and advantages of the present invention will bemore fully understood by reference to the following detailed descriptionin conjunction with the attached drawings in which like referencenumerals refer to like elements through the different views. Thedrawings illustrate principals of the invention and, although not toscale, show relative dimensions.

FIG. 1 is a perspective view of a split mechanical seal separated intotwo segments according to a preferred embodiment of the invention;

FIG. 2 is a cross-sectional view of the mechanical seal of FIG. 1according to one embodiment of the invention;

FIG. 3 is a fragmentary cross-section view of the mechanical seal ofFIG. 1;

FIG. 4 is an exploded unassembled view of one half of the mechanicalseal of FIG. 1 taken along line 3-3;

FIG. 5 is a perspective view of one-half of the mechanical seal of FIG.1;

FIG. 6 is a perspective view of an axially outer portion of the rotaryseal ring holder of the mechanical seal of FIG. 1 according to oneillustrative embodiment of the invention;

FIG. 7 is a cross-sectional view of the rotary seal ring holder of FIG.6;

FIG. 8 is a cross-sectional view of a portion of the rotary seal ringholder of FIG. 6;

FIG. 9 is a cross-sectional detailed view of the rotary seal ring holderof FIG. 6, diagramming particular angles and lengths according to oneembodiment of the invention;

FIG. 10 is a side view of a gland assembly suitable for use in themechanical seal assembly according to an illustrative embodiment of theinvention;

FIG. 11 is another side view of the gland assembly of FIG. 10;

FIG. 12 is a perspective view of the gland assembly of FIG. 10;

FIG. 13 is a perspective view of one segment of the gland assemblyshowing the overlapping interfacing surfaces of both ends of the glandsegment;

FIG. 14 is a detailed, close-up view of an interfacing region of thegland assembly according to an illustrative embodiment of the invention;

FIG. 15 is a detailed, close-up view of the gland segments at theoverlapping, interacting surfaces;

FIG. 16A is a side view of a gland or holder screw according to anembodiment of the invention;

FIG. 16B is a broken perspective view of the screw housing of FIG. 1according to an embodiment of the invention;

FIG. 17 is a sectional view of an elastomeric member; and

FIG. 18 is a plan view of a holder assembly according to a preferredembodiment of the invention;

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

The present invention provides a mechanical seal assembly for providingsealing on a rotating shaft or other suitable device. The invention willbe described below relative to illustrated embodiments. Those skilled inthe art will appreciate that the present invention may be implemented ina number of different applications and embodiments and is notspecifically limited in its application to the particular embodimentdepicted herein.

The terms “seal assembly” and “sealing assembly” as used herein areintended to include various types of sealing assemblies, includingsingle seals, split seals, concentric seals, spiral seals, and otherknown seal and sealing assembly types and configurations.

The term “shaft” is intended to refer to any suitable device in amechanical system to which a seal can be mounted and includes shafts,rods and other known devices.

The terms “axial” and “axially” used herein refer to a directiongenerally parallel to the axis of a shaft. The terms “radial” and“radially” used herein refer to a direction generally perpendicular tothe axis of a shaft. The terms “fluid” and “fluids” refer to liquids,gases, and combinations thereof.

The term “axially inner” as used herein refers to the portion ofstationary equipment and a seal assembly proximate the mechanical systememploying the seal assembly. Conversely, the term “axially outer” asused herein refers to the portion of stationary equipment and a sealassembly distal from the mechanical system.

The term “radially inner” as used herein refers to the portion of theseal assembly proximate a shaft. Conversely, the term “radially outer”as used herein refers to the portion of the seal assembly distal from ashaft.

The terms “stationary equipment”, “static surface” and “gland” as usedherein are intended to include any suitable stationary structure housinga shaft or rod to which a seal is secured.

The mechanical seal assembly of an illustrative embodiment of theinvention may employ an improved rotary seal ring holder for mountingand holding a rotary sealing member in a selected position within themechanical seal assembly and/or an improved gland assembly forconnecting stationary components of the mechanical seal assembly tostationary equipment.

The rotary seal ring holder in the mechanical seal ring assembly mayemploy a groove on a radially inner surface thereof. The groove isdesigned and configured to seat, catch or retain a sealing element usedto seal against a radially outer surface of the rotary sealing member,such as a rotary seal ring. The groove keeps the sealing element and theassociated rotary seal face in place to improve sealing and the overalllife of the mechanical seal assembly. The groove also preferablycaptures the sealing element and the rotary seal face in a preciselocation so that the rotary seal face remains seated substantiallyperpendicular to the shaft axis.

The rotary seal ring holder has an axially-extending opening formed atan axially outer end thereof for receiving the rotary sealing member andO-ring. The axially-extending opening preferably tapers from a widediameter at the axially outer end to a narrower opening where the rotarysealing member and O-ring are seated. The axially-extending opening inthe rotary seal ring holder may taper in at least two stages. In oneembodiment, described in detail below, the axially-ending receivingcomprises a double-angled tapering inner surface that leads from theaxially outer end of the rotary seal ring holder to the detent groove onthe radially inner surface. The use of two angled faces on the radiallyinner surface reduces an insertion force necessary for inserting theO-ring into a space between the rotary seal ring holder and the rotarysealing member.

The seal gland assembly of the mechanical seal assembly may employoverlapping gland halves that interlock to prevent sliding of the glandhalves relative to each other during operation.

FIGS. 1-5 depict a split mechanical seal 10 according to a preferredembodiment of the present invention. The mechanical seal 10 ispreferably concentrically disposed about a shaft 12 that extends along afirst axis 13 and is secured to an external wall of a housing 14, suchas a pump or other system. The shaft 12 may be mounted, at least partly,within or adjacent to the housing. The mechanical seal 10 constructed inaccordance with the teachings of this invention provides a fluid-tightseal, thereby preventing a process medium, e.g., hydraulic fluid, fromescaping the housing 14. The fluid-tight seal is achieved by sealingmembers, illustrated as a pair of seal rings 20 and 30. The illustrativesealing members include a first or rotating seal ring 20 and a second orstationary seal ring 30 that form a seal therebetween. Each seal ring 20and 30 has a smooth arcuate sealing surface 21, 31, respectively. Thesmooth arcuate sealing surface 21, 31 of each seal ring is biased intosealing contact with the corresponding sealing surface 21 or 31 of theother seal ring. Preferably, the seal rings 20 and 30 are split intosegments 25, 25′ and 30, 30′, respectively, to facilitate installation,as described below. The sealing surfaces of the seal rings provide afluid-tight seal operable under a wide range of operating conditions,including a vacuum condition, as described in greater detail below

The illustrated mechanical seal 10 includes, in addition to the rotaryseal ring 20 and the stationary seal ring 30, a seal gland assembly 40for mounting stationary seal components to the equipment 14, and a sealring holder assembly 110 for mounting the rotary seal ring 20, describedin further detail below.

The holder assembly 110 defines a space 201 for receiving and retainingthe rotary seal ring 20. The holder assembly 110 may be split tofacilitate assembly and installation. In one embodiment, the holderassembly 110 comprises a pair of segments 112, 114 that mate to form theannular holder assembly 100. The holder assembly 110, or each holdersegment if the holder assembly is split, has a radially outer surface116 facing the gland assembly 40 and a radially inner surface 124 forsealing against the shaft and defining the space 201 for receiving andretaining the rotary seal ring 20. The holder assembly 110 forms anaxially-extending annular opening at the axially outer end 111 leadingto the space 201 to allow insertion of the rotary seal ring 20 into thespace.

A sealing element, such as O-ring 188, is concentrically disposed aboutthe rotary seal ring 20 to seal between the rotary seal ring 20 and theholder 110. As shown, the O-ring is preferably disposed about a radiallyouter surface 184 of an axially inner portion of the rotary seal ring20, as described below, and seals against the radially inner surface 124of the holder assembly 110. As described in detail below, the radiallyinner surface 124 of the holder assembly 110 may include a detent groove189 for receiving and seating the O-ring 188 disposed about the rotaryseal ring 20 to facilitate assembly and operation of the seal assemblyand maintain the rotary seal ring 20 in an optimal position.

Other sealing members may seal the interfaces between differentcomponents of the mechanical seal assembly 10. For example, in theillustrative embodiment, a flat, annular elastomeric gasket 60 seals theinterface between the seal gland assembly 40 and the housing 14. Aholder gasket 160 seals two halves of a holder assembly 110, if theholder assembly 110 is split, as described below. A holder/shaftelastomeric member, illustrate as O-ring 142 seals between the rotaryseal ring holder assembly 110 and the shaft 12. A stationary sealring/gland elastomeric member, illustrated as O-ring 202, seals at aninterface between the stationary seal ring 30 and the gland assembly 40and provides radially inward pressure on the stationary seal ring 30.One skilled in the art will recognize that the mechanical seal assemblymay have any suitable means for sealing between different components.

In addition, the illustrative seal assembly 10 may also include ananti-rotation pin 144 extending axially between the rotary seal ring 20and the holder assembly 110, as described below, to prevent relativerotary movement of the rotary seal ring and holder assembly. As shown inthe embodiment of FIG. 2, a centering button 74 disposed between theradially outer surface 116 of the seal ring holder assembly 110 and thegland assembly 40 may be included to facilitate centering of the sealassembly around the shaft 12. As also shown in FIG. 2, a first sockethead screw cap 181 secures the holder assembly 110, while a secondsocket head screw cap 183 secures the gland assembly 40. SB bolts 67 andbolt tabs 38 secure the gland assembly 40 to the equipment 14, asdescribed in detail below.

Certain components of the illustrative seal assembly of the illustrativeembodiments of the invention are similar to the mechanical seal assemblydescribed in U.S. Pat. No. 5,571,268, the contents of which are hereinincorporated by reference.

As illustrated in FIGS. 1-5, the holder assembly 110 for mounting therotary seal ring 20 is disposed in a chamber 24 formed by the glandassembly 40, and spaced radially inward therefrom. It should beunderstood however, that the holder assembly 110 need not be disposedwithin the gland assembly 40. Rather, the holder assembly 110 can beaxially spaced from the gland assembly 40.

The holder assembly 110 is designed and configured to facilitateinstallation of the rotary seal ring 20 therein, as well as overalloperation of the mechanical seal. According to an illustrativeembodiment, the radially inner surface 124 of the holder assembly 110 isconfigured to facilitate installation of the rotary seal ring 20 in theholder assembly 110 and improved squaring of the rotary seal face 21 tothe shaft 12.

FIGS. 6-9 illustrate the holder assembly 110 of one embodiment of theinvention in greater detail. FIG. 6 is a perspective view of the axiallyouter end 111 of the holder assembly 110. As shown, the holder assemblyradially inner surface 124 includes two sloped faces 124 a, 124 bextending from the axially outer end 111, such that the inner surface124 tapers through two stages from a relatively wide opening at theaxially outer end 111 to the narrower space 201 for receiving the rotaryseal ring 20. As shown, the radially inner surface 124 thus forms adouble angled lead-in chamfer extending from the axially outer end 111of the holder 110 along the inner wall to the groove 189. In theillustrative embodiment, the first sloped face 124 a comprising thefirst stage forms a radially inward face that slopes radially inwardfrom the front, radially-extending wall 1121 at the axially outer end111 of the holder assembly 110. The first sloped face terminates at, andtransitions into, the second sloped face 124 b. The second sloped face124 b comprising the second stage extends radially inward at a slopefrom the first sloped face 124 a and terminates in an axially-extendingflat face 124 c, or other intermediate surface. The illustrativeintermediate surface 124 c extends generally parallel to the axis 13.The intermediate surface, such as flat face 124 c in turn extends to andintersects a stepped, axially inward-extending wall 132, defining theaxially inner end of the space 201 for receiving the rotary seal ring20. Alternatively, the holder assembly 110 can omit theaxially-extending flat face 124 c, such that the second sloped face 124b extends to and intersects with axially inward extending wall 132.Furthermore, those of ordinary skill in the art will recognize that thelead-in chamfer to the space 201 at the axially outer end 111 of theinner surface 124 may include more than two radially inward slopingfaces.

The multi-angled lead-in chamfer facilitates insertion of the rotaryseal ring 20 and O-ring 188 in the space 201 while the holder 110 iscoupled to the shaft 12.

As shown in detail in FIG. 9, the first radially inwardly sloped face124 a extends at a first angle θ transverse to an axis, illustrated byphantom line L, which is parallel to the axis 13 and which intersectsthe axially extending radial flat face 124 c or the axially extendinginner side of the space 201 if the holder does not include the flat face124 c. In the illustrative embodiment, the first angle θ at which thefirst radially inward sloped face 124 a extends is between about 10degrees and about 20 degrees and is preferably about 15 degrees withrespect to the phantom line L. One skilled in the art will recognizethat the first radially inward sloping face 124 a may extend at anysuitable angle and is not limited to the illustrative range.

The second radially inward sloped face 124 b extends at a second angleθ′ that slopes relative to the axis L, as shown in FIG. 9. In theillustrative embodiment, the second angle θ′ is smaller than the firstangle θ. The illustrative second angle θ′ extends between about 2 andabout 10 degrees and is preferably between about 3 and about 4 degreesand most preferably about 3.5 degrees relative to the phantom line L.One skilled in the art will recognize that the second radially inwardsloping face 124 b may extend at any suitable angle and is not limitedto the illustrative range.

As shown in FIG. 9, the interface/transition point 1240 between angledfaces 124 a and 124 b is preferably spaced a selected distance T fromthe wall 132. The front, radially-extending wall 1121 at the axiallyouter end 111 of the holder assembly 110 is spaced from the wall 132 bya distance F. The particular distances may be selected according to theparticular application, size of the O-ring 188 used, size of the overallseal and other factors, and can be easily determined by one skilled inthe art. One skilled in the art will recognize that the angled and flatsurfaces of the inner surface 124 may have any suitable configuration,length and distance from other components of the holder assembly 110 andthat the invention is not limited to the illustrative embodiment.

A pair of successive radially inward stepped surfaces forms a second,axially extending, face 134 and a third, axially extending, face 138,respectively, of the rotary seal ring holder 110. The radially innersurface 124 and the third face 134 have a radially inward-extendingfirst wall 132 integrally formed therebetween. In the illustrativeembodiment, an axially-extending flat (i.e., non-sloped) face 124 c, orother intermediate surface, extends between the second radially inwardsloping face 124 b and the radially-extending first wall 132. In analternative embodiment, the second radially inward sloping face 124 bextends to and terminates in the radially-extending first wall 132. Asshown, the third face 134 and the fourth face 138 have a radially inwardextending second wall 136 integrally formed therebetween. The diameterof the fourth face 138 is preferably equal to or slightly greater thanthe diameter of the shaft 12, to which the holder assembly 110 is to beattached.

In a preferred embodiment, the O-ring 188 for sealing between the rotaryseal ring 20 and the rotary seal ring holder 110 seats in a groove 189,such as a detent groove, formed on the radially inner surface 124 of theholder assembly 110. The detent groove 189 is sized, located andconfigured to receive a top, radially outer side of the O-ring 188 toseat the O-ring 188 relative the holder assembly 110 during installationwithout compromising performance. The detent groove 189 preferably seatsthe O-ring 188 at the intersection of the first wall 132 and radiallyinner surface 124 of the holder assembly, such that the O-ringpreferably contacts, or is in close proximity with, the first wall 132,the inner surface 124 and the radially outer surface 184 of the rotaryseal ring 20. Alternatively, the detent groove 189 seats the O-ring inanother location between the rotary seal ring holder assembly 110 andthe rotary seal ring 20.

When seated in the detent groove 189, the O-ring preferably abuts thesecond and third outer surfaces 182, 184 of the rotary seal ring 20, asshown in FIGS. 2-4.

In the illustrative embodiment, the detent groove 189 is formed on thesecond radially-inwardly sloping face 124 b of the holder assembly 110.In the embodiment shown in FIG. 9, the axially inner end 189 a of thedetent groove 189 aligns with the axially inner end of the secondradially-inwardly sloping face 124 b (i.e., where the secondradially-inwardly sloping face 124 b intersects the axially-extendingflat face 124 c).

In the illustrative embodiment, the slope of the angle θ′ for the secondradially-inward sloping face 124 b preferably starts at the axiallyinner side 189 a of the detent groove 189. In this manner, the axiallyouter side 189 b of the detent groove 189 is radially outward of theaxially inner side 189 a of the detent groove 189, due to the slope inthe surface where the detent groove 189 is formed.

Alternatively, the detent groove 189 may be formed on another face ofthe radially inner surface 124, preferably spaced from the wall 132 tofacilitate sealing against the rotary seal ring 20.

The detent groove 189 is relatively shallow and preferably has a depthsignificantly less than the nominal diameter D′ of the O-ring 188. Forexample, in the illustrative embodiment, the detent groove is a shallow,curved annular depression in the surface of the inwardly sloping face124 b. The illustrative detent groove 189 is curved in two dimensions(preferably radially and axially), forming a surface similar to aradially outer half of a torus to match the radially outer surface ofthe O-ring 188. The detent groove 189 is preferably sized anddimensioned to seat and retain the O-ring 188 in an optimal position. Inthe illustrative embodiment, the detent extends a depth D from the flatface 124 c on the radially inner surface 124 of the holder assembly 110.The ratio of the depth D to the nominal diameter D′ of the associatedO-ring 189 is preferably between about 0.02 and about 0.10, and morepreferably between about 0.03 and about 0.05. The detent groove 189 hasa shape across the width W formed by an arc having a radius R. The ratioof the radius R forming the detent groove 189 and the nominal diameterD′ of the associated O-ring 188 that seats in the groove 189 ispreferably between about 0.25 and about 0.50 and preferably betweenabout 0.3 and about 0.4 and most preferably between about 0.33 and about0.38. One skilled in the art will recognize that the detent groove 189is not limited to this size, shape and configuration and may have anysuitable size, shape and configuration suitable for retaining anassociated O-ring 189 disposed about a rotary seal ring 20.

The axially inner end 189 a of the detent groove 189 is preferablyspaced from the radially-extending wall 132 by a distance I. The centerof the detent groove 189 is spaced a distance C from the wall 132. Oneskilled in the art will be able to determine a suitable configuration,location and size of the detent groove 189 to properly position theO-ring 188. One skilled in the art will recognize that the invention isnot limited to locating the detent groove 189 in the illustrativelocation and that the detent groove may be located at any suitablelocation on the radially inner surface 124 of the holder assembly.

The O-ring 188 seated by the detent groove 189 is preferablysufficiently resilient to place each of the rotary segment sealing facesin sealing contact with another segment, thereby forming a fluid-tightand pressure-tight seal. The O-ring 188 also functions, in cooperationwith a biasing member, such as a spring, illustrated as a mechanicalclip 200, as an axial resilient biasing means by floatingly andnon-rigidly supporting the rotary seal ring 20 and the stationary sealrings 30 in axially spaced floating relation relative to the rigid wallsand faces of the gland and holder assemblies 40, 110. This floatingrelationship was first described in U.S. Pat. No. 4,576,384, assigned tothe assignee hereof, and is herein incorporated by reference.

The rotary seal ring 20 and O-ring 188 are inserted into the space 201after the holder 110 is assembled on the shaft 12. Due to thedouble-tapered surface at the lead-in chamfer of the radially innersurface 124, less force is required to install the rotary seal ring 20and O-ring 188 into position. The detent groove 189 receives andautomatically centers the O-ring 188, placing the rotary seal surface 21into position perpendicular to the axis of the shaft 12. The describedconfiguration of the holder, with the multi-angled lead-in surface anddetent groove reduces or eliminates the need to hold the seal face inposition during installation.

The detent groove 189 allows for a rotary seal ring 20 with an O-ring188 disposed already about the outer diameter to be inserted into thealready tightened holder 110 by sliding the rotary seal ring/O-ringassembly axially into the holder 110 through the space 201 formedbetween the radially inner surface 124 and the shaft 12. The detentgroove captures the O-ring to keep it in place during this assemblyprocess. The design of the illustrative holder allows for the holderassembly 110 to be first tightened around the shaft 12, followed byinsertion of the seal ring and O-ring The detent groove 189 thusfacilitates the assembly of the face and elastomer inside the alreadytightened clamping holder 10.

Alternatively, the detent groove 189 may be formed on a radially innersurface of the holder assembly 110 that does not include thedouble-angled lead-in chamfer.

Referring back to FIGS. 3, 4 and 7, the holder segment outer surface 116of the holder assembly 110 may have a first axially extending outersurface 146, a radially inward sloping second outer surface 148, and aradially inward stepped third outer surface 154. The third outer surface154 and the second outer surface 148 form, in combination, a radiallyinward extending first outer wall 150. The outer surfaces of the holderassembly 110 are preferably spaced from the inner surfaces 54, 56 of thegland assembly 40. As shown in FIGS. 2 and 3, the first axiallyextending outer surface 146 faces an axially-extending inner gland face54 on the gland 40, with the outer diameter of the first outer surface146 being preferably less than the inner diameter of gland segment face54. In a preferred embodiment, the outer diameter of the holder segmentthird outer surface 154 is less than the diameter of a face 56 of thegland segment opposite the surface 154 when the mechanical seal isassembled. This clearance allows the holder assembly 110 to seat withinthe gland assembly 40 for unobstructed rotational movement therein.

The fourth face 138 on the inner surface of the holder segment 112 hasformed thereon an annular channel 140 for mounting a split shaft gasket,illustrated as O-ring 142. When mounted in the channel 140, the gasket142 sealingly mates with the shaft 12, providing a fluid-tight sealalong the holder and shaft interface (see FIGS. 2 and 3). The secondwall 136 preferably has axially extending therefrom a cylindricalprotrusion forming the anti-rotation pin 144. The protrusion 144operates as a mechanical rotary means by biasing the rotary seal ring 20into rotational movement, as described in greater detail below.

The holder segments 112, 114 may also have formed on each split holderseal face 118 and 120 a holder gasket groove 158, having theconfiguration illustrated in FIGS. 1-5. A holder gasket 160,complementary in shape to the groove 158, seats in groove 158. Theholder gasket 160, when seated in the groove 158, may extend beyond theholder seal faces 118, 120, as best shown in FIG. 5. The exposed portionof the gasket 160 seats in a complementary groove formed in the oppositeholder segment seal face. This arrangement provides for a fluid-tightseal at pressures higher than a selected value, as described above. Thegasket is preferably composed of any suitable deformable material, suchas elastomeric rubber.

The holder segments 112, 114 may also have a fastener-receiving aperture164 that mounts screw 170 for securing the holder segments 112, 114together. The screws 170 are mounted in and positively maintained by thefastener-receiving apertures 164.

The rotary seal ring assembly 20 also may include a pair of arcuaterotary seal ring segments 25, 25′, while the stationary seal ringassembly may include a pair of arcuate stationary seal ring segments 33,33′. Each seal ring segment has a smooth arcuate sealing surface 21, 31,respectively, and a pair of segment sealing faces 22, 32, respectively.The smooth arcuate sealing surface 21, 31 of each seal ring is biasedinto sealing contact with the corresponding surface 21, 31′,respectively, of the other seal ring segment to create a fluid-tightseal. Similarly, the segment sealing faces 22, 32 of the ring segments25 and 33 are biased into sealed relationship with each other to formeach of the seal rings 20 and 30. Thus, these individual seal facesprovide a fluid-tight seal operable under a wide range of operatingconditions, including a vacuum condition.

The illustrative rotary sealing element 20, illustrated as arcuaterotary seal ring segments 25, preferably has a substantially smootharcuate inner surface 172 and an outer surface comprising severalsurfaces 180, 182, 184, as best shown in FIG. 4. The inner surface 172may have formed thereon a generally rectangular notch 174. The notch 174mounts over the holder protrusion 144. The illustrative rotary segmentouter surface has an axially extending first outer surface 180 thatterminates in a radially inward sloping second outer surface 182 orabutment, and an axially extending third outer surface 184, about whichthe O-ring 188 is disposed. The rotary segment 25 also preferably hasthe smooth arcuate sealing surface 21 disposed at the top of the ring20. The inner diameter of the rotary seal segments inner surface 172 isgreater than the diameter of the shaft to permit mounting thereon. Thediameter of the rotary seal segment third outer surface 184 is equal toor slightly less than the diameter of the holder segment third face 134,for mounting engagement with the holder assembly 110. The diameter ofthe rotary seal segment first outer surface 180 is less than the innerdiameter of the holder segment tapering inner surfaces 124 a, 124 b, andgreater than the diameter of the holder third face 134. One skilled inthe art will recognize that the rotary seal ring 20 may have anysuitable configuration for interfacing with and sealing against anothersealing element, such as the stationary seal ring 30.

Although the illustrated seal ring 20 has an abutment 182 formed at theouter surface, those of ordinary skill will recognize that a non-slopingstepped annular surface could also be employed.

As best shown in FIG. 4, the illustrative stationary seal ring 30 maysimilarly include a pair of arcuate seal ring segments 33, 33′, eachidentical or substantially identical to the other. The illustrativestationary seal ring arcuate segments 33 have a substantially smootharcuate inner surface 35 extending parallel to the first axis 13 and anouter surface 36. The stationary seal ring segment outer surface 36preferably has an axially extending first outer surface 190 thatterminates in a radially outward extending abutment 192. The stationaryseal ring 30 preferably has a substantially smooth arcuate top surface194 and a smooth arcuate ring sealing surface 31 disposed at the bottomof the ring. The illustrative stationary seal segment 33 also has arecess 196 formed along the top surface 194. A mechanical clip 200,mechanically coupled to a top surface 62 of the gland assembly 40 via aclip groove 63, seats in the recess 196. This arrangement helps alignand seat the stationary seal ring 30 in the chamber 24, as well asfunctioning as a mechanical impedance for preventing the stationary sealring 30 from rotating with the shaft 12 and the rotary seal ring 20.

The inside diameter of the stationary segment inner surface 35 isgreater than the shaft diameter, and is greater than the diameter of theinner surface 172 of the rotary seal ring 20, thereby allowing relativemotion therebetween. Therefore, the stationary seal ring 30 staysstationary while the shaft 12 rotates. An elastomeric member, e.g.,O-ring 202, provides a radially inward biasing force sufficient to placethe segment sealing faces 32 of stationary seal ring segment 33 insealing contact with the other stationary seal ring segment.Additionally, O-ring 202 forms a fluid-tight and pressure-tight sealbetween the gland assembly 40 and the stationary seal ring 30. TheO-ring 202 seats in a first mounting region 204 defined by the glandsegment first wall 48, the gland second face 50, the stationary ringouter surface 190, and the stationary ring abutment 192. In a preferredembodiment, the abutment 192 forms an angle relative to the stationaryring outer surface 190 preferably in the range of about 30° to about60°, and most preferably about 45°. The stationary seal ring 30 ispreferably composed of a carbon or ceramic material, such as alumina orsilicon carbide and the like.

The biasing member, illustrated as a mechanical clip 200 in theillustrative embodiment, also functions as an axial biasing means byproviding resilient support for the stationary and rotary seal rings 20,30 by axially biasing the seal rings such that the stationary and rotarysealing surfaces 21 and 31 are disposed in sealing contact with eachother. As illustrated in FIG. 3, the seal rings 20, 30 are floatinglyand non-rigidly supported in spaced floating relation relative to therigid walls and faces of the gland and holder assemblies 40, 110. Thisfloating and non-rigid support and spaced relationship permits smallradial and axial floating movements of the rotary seal segments 25, 25′and the stationary seal segments 33, 33′ with respect to the shaft 12,while still allowing the rotary sealing surface 21 to follow and to beplaced in sealing contact with the smooth arcuate sealing surface 31 ofthe stationary seal ring 30. Thus, the rotary and stationary seal ringsealing surfaces 21 and 31 are self-aligning as a result of thisfloating action.

The illustrative mechanical seal assembly 10 may also include animproved seal gland assembly 40 to improve operation of the sealassembly, as shown in FIGS. 10-15. The illustrative seal gland assembly40 has a pair of gland segments 41, 42 that mate to form the annularseal gland assembly 40.

In the illustrative embodiment, as shown in FIG. 10-15 the glandsegments 41, 42 are configured to engage each other to facilitateassembly and operation of the mechanical seal assembly. The illustrativegland assembly segments 41, 42 have an interlock mechanism to facilitateengagement of the two segments 41, 42. In contrast to prior glanddesigns, each gland segment 41, 42 has at least one non-flat, shapedinterfacing surface 64, 66 to transmit a bolting force to the othermating gland half and prevent sliding of the gland halves relative toeach other. In the illustrative embodiment, the gland segmentinterfacing surfaces have stepped faces forming interlocking protrusions411, 421, respectively, and recesses 413, 423, respectively formed on atleast one interface between the two segments. Each protrusion 411, 421fits into the corresponding recess 413, 423 such that an overlap 1000between the two segment interfacing surfaces forms to engage thecorresponding gland segment. The raised surface transmits the boltingforce applied to the gland and facilitates connection and alignment ofthe gland segment halves. The overlapping components reduce and/orprevent a separation force at the gland splits caused by bolt glandsthat bolt the gland assembly to the equipment housing.

In the illustrative embodiment, as shown in FIGS. 11 and 14, eachinterfacing surface is a stepped surface having a flat, axiallyextending face 4110, 4210 and a flat, radially-extending face 4111, 4210extending perpendicular from each flat, axially-extending face 4110,4210, respectively, to define the protrusion 411, 421. The flat,radially-extending faces 4111, 4210, extend to flat, axially extendingfaces 4112, 4212 stepped from and parallel to the faces 4110, 4210 todefine the recesses 413, 423 on each interfacing surface. Preferably,the flat, axially extending surfaces, 4111, 4210, which mate to form theoverlap 1000, extend substantially perpendicular to the longitudinalaxis 13 of the mechanical seal assembly, thereby allowing a bolt forcetranslated to the gland segments to transmit to the other gland segmentwithout causing separation of the gland segments. One skilled in the artwill recognize that the protrusions and corresponding recesses may haveany suitable configuration.

Those of ordinary skill will readily recognize that other interfacingand/or interlocking arrangements can be employed. For example, eachinterfacing surface may have several protrusions and/or recesses, orotherwise-formed overlapping surfaces, which may be formed at anysuitable location on the interfacing surfaces.

Referring to FIGS. 3, 4, 13 and 14, each illustrative gland segment 42may have an inner surface that has a first face 46, and an integrallyformed and stepped second face 50 that extends radially outward from thefirst face 46. The first face 46 and the second face 50 form, incombination, a first connecting annular wall 48. A stepped third face 54extends radially outward from the second face 50 and forms, incombination therewith, a second annular connecting wall 52, which may bestepped, and/or include a sloping surface extending to the second face50. A sloped fourth face 56 extends radially inward from the glandsegment third face 54. The gland segment inner surface formed by faces46, 50, 52, 54 and 56 defines the space 24 for receiving the holderassembly 110, as described above.

As shown in FIG. 13, the second gland seal face 66′ of the gland segment42 may also be shaped to interlock with a correspondingly shaped secondgland seal face (not shown) of the first gland segment 41. In theillustrative embodiment, the second gland seal face 66′ also includes aprotrusion 421, and a recess 423, which are positioned opposite theprotrusion and recess on the first gland seal face 66.

Each gland seal face 64, 66, 66′ may also have formed thereon a glandgasket groove 70. FIG. 14 illustrates the gland seal face 64 of thefirst gland segment in detail, illustrating the groove 70. Theillustrative groove 70 has a main axial portion 71 which extends fromthe gland second face 50 to the gland fourth face 56. Groove segments72, 73, transverse to the main groove segment 71, extend along thesecond gland wall 52 and the gland fourth face 56, respectively, andgroove segment 74, spaced radially inward from groove segment 71,extends along the gland segment second face 50.

An elastomeric gland gasket 76, complementary in shape to the glandgroove 70, seats in the groove 70 of the gland. The gasket 76, whenseated in the groove 70, may extend beyond the gland split faces 64, 66,as best shown in FIGS. 1, 4 and 5. The exposed portion of the gasket 76is captured in a complementary groove formed on the split gland sealface of the other gland segment 42 when the gland segments 41, 42 areassembled. Capturing both ends of the gasket 76 between opposing splitgland seal faces prevents the gasket 76 from extruding into the gapformed between the split gland seal faces when subjected to pressureshigher than a selected maximum pressure. This double-capturing featurethus allows the gland segments 41, 42 to withstand greater pressureswithout developing pressure leaks, as well as relaxing the mechanicaltolerances of other components of the mechanical seal 10. The glandgasket 76 is preferably formed from any suitable resilient material,such as elastomeric rubber. Further, although the gasket 76 has theillustrated shape, those of ordinary skill will recognize that thegasket 76 and its corresponding groove 70 can have any suitablegeometric configuration.

Each of the gland segments 41, 42 may also have integrally formedtherewith a pair of screw housings 80, 82. Each screw housing has atransverse fastener-receiving aperture 84 formed substantiallytherethrough. The aperture 84 has a tapped smaller-diameter portion 86,and a concentric untapped larger-diameter portion 88, as shown in FIGS.1, 16A and 16B. Preferably, the untapped portion 88 of the aperture 84is disposed closest to the gland seal faces 64, 66.

The transverse aperture 84 mounts a screw 90 having the illustratedconfiguration. The screw 90 preferably has a main shaft 92 and ascrew-head portion 96. The screw shaft 92 has a threaded distal portion93 and an untapped proximal portion 94, as shown in FIGS. 1 and 16A. Theouter diameter of the threaded portion 93 is greater than the outerdiameter of the proximal portion 94. As illustrated in FIG. 16B, eachscrew 90 fastens together a pair of housings 80 and 82. When thethreaded distal portion 93 of the screw 90 is screwed into the tappedportion 86 of the aperture 84, the distal portion 93 is positivelymaintained in the aperture 84. As the screw 90 further travels throughthe aperture 84, the screw distal end enters the untapped portion 88, orclearance gap of the aperture 84. In this orientation, the screw 90,although not snugly secured, is still positively maintained (i.e., notdetachable) in the aperture 84. In a preferred embodiment, the diameterof the screw distal portion 93 is close to the diameter of the tappedsmaller-diameter portion 86 of the screw housings 80,82.

Significant advantages are enjoyed by the screw 90 and the aperture 84of the present invention. In particular, the screw 90 can be mounted inthe fastener-receiving aperture 84 from any side of either gland segment41, 42 prior to assembly, which is particularly useful in limited accessinstallations, and is positively maintained in the screw housing 80. Bypreventing the screw 90 from completely detaching from the screw housing80 prevents accidental loss of the screw 90 during assembly anddisassembly, thus facilitating assembly of the seal while reducinginstallation time. The same construction pertains to the screw housings82.

The gland assembly 40 may also have a housing gasket groove 58 formedalong a bottom 59 of the gland assembly 40. The groove 58 seats theflat, annular elastomeric gasket 60. As illustrated in FIGS. 3 and 4,the gasket 60 preferably has an axial dimension greater than the depthof the groove 58, thereby providing a pressure-tight and fluid-tightseal between the mechanical seal 10 and the housing 14. In a preferredembodiment, the housing gasket 60 is pre-cut into two arcuate segmentsfor mounting in each gland segment 41, 42. The housing gasket segmentsare preferably mounted in the groove 58 and secured thereto by anadhesive. This arrangement helps prevent leakage of the process mediumalong the seal 10 when mounted to the housing 14.

The illustrative gland assembly 40 may further include a plurality ofbolt-tabs 38. The bolt-tabs 38 have a main body 37 that has integrallyformed at one end an inserting-tab projection 39. The tab projection 39mounts in an annular groove 68 formed around the periphery of the glandassembly 40. The angular position of the tabs can be adjusted by slidingthe bolt-tab 38 and the tab projection 39 about the groove 68. Thebolt-tabs 38 help secure the mechanical seal 10 to the housing 14 byseating mounting bolts (not shown). In use, the mounting bolt isinserted between a pair of adjacent bolt-tabs. The bolt-tabs 38 arefurther described in detail in U.S. Pat. No. 5,209,496, assigned to theassignee hereof and which is herein incorporated by reference.

The holder assembly 110, the gland assembly 40, and the screws 90 can beformed from any suitably rigid material, such as stainless steel.

In one embodiment of the invention, the O-rings 188 and 202 may be splitto facilitate assembly as well. As generally illustrated in FIG. 17,identical ball and socket fastening mechanisms may be provided on thefree ends of O-rings 188 and 202. At one end, O-ring 202 narrows into asubstantially hemispherical shoulder portion 222 and, adjacent thereto,annular neck portion 224. Immediately adjacent neck portion 224 is asubstantially spherical head portion 226. In fastening, head portion 224is inserted into matching spherical socket portion 227 at the other endof O-ring 202 such that annular collar portion 228 surrounds andcaptures neck portion 224, and shoulder portion 222 is in intimatecontact with annular jacket portion 230. Additionally, although themechanical seal 10 and its associated components are depicted assectional parts, the O-rings 188 and 202 are continuous and completestructures having the above configuration. However, the O-rings 188 and202 are not limited to the illustrative embodiment and may have anysuitable configuration. For example, the O-rings 188 and 202 may besolid or have an alternative fastening mechanism.

In assembly, the O-ring 188 is concentrically disposed about the rotaryseal segments 25, preferably in contact with the rotary seal outersurfaces 182, 184, and the rotary seal segments 25, 25′ then are mountedin the holder assembly 110, preferably already disposed about the shaft12, by aligning the rectangular notch 174 of the rotary seal ringsegment 25 with the axially extending anti-rotation holder protrusion144. The O-ring disposed about the rotary segments 25 is further placedin sealing contact with the holder inner surface, preferably in theaxially-extending flat face 124 c, the holder first wall 132. Asdescribed above, the detent groove 189 receives and retains the O-ring188, and the associated rotary seal ring 20, in an optimal position,while the multi-angled lead-in chamfer facilitates insertion of theO-ring 188 and rotary seal ring into the holder assembly 110. The O-ring188 provides an inward radial force sufficient to place the rotary sealfaces 22 of the seal segment 25 in sealing contact with each of thesealing faces 22 of the other rotary segment. The holder segments112,114 are then secured together by tightening the screws 170 that arepositively maintained in the fastener-receiving apertures 164. As shownin FIGS. 1-4, the rotary seal ring segments 25, 25′ are spaced from theholder assembly inner surfaces 124, and are non-rigidly supportedtherein by the O-ring 188, thereby permitting small radial and axialfloating movements of the rotary seal ring 20.

The stationary seal ring segments 33 are concentrically mounted over theshaft 12, and secured together by O-ring 202. The O-ring 202 applies aradially inward force to the stationary seal ring outer surface 36sufficient to place the segment sealing faces 32 of each segment insealing contact with each other.

The gland segments 41,42 are concentrically placed about the holderassembly 110, such that the faces engage, and the rotary and stationaryseal rings 20,30, and are secured together by screws 90 that are mountedin and positively maintained by the fastener-receiving apertures in thescrew housings 80 and 82. The screws 90 cannot be unintentionallyremoved from the mechanical seal 10 since they are secured to the glandassembly 40 by the inventive fastener-receiving aperture 84 and screw90. Additionally, mounting the screws 90 does not necessitate rotatingthe shaft since the screws 90 can be secured from the same or oppositesides of the gland assembly 40.

Prior to fully securing the gland screws 90 to the housing 14, the shaft12, the holder assembly 110, and the rotary and stationary seal rings20, 30 should be centered within the chamber 24. As described above, thedetent groove 189 facilitates centering of the rotary seal ring 20. Inaddition, centering spacers 240, may be optionally be provided along theouter surface 116 of the holder assembly 110, as shown in FIG. 18 tocenter the gland segments 41, 42 by way of centering spacers 240 formed.The spacers can be integrally formed on the holder outer surface 116, orcan be mounted in depressions formed along the holder outer surface 116.In a preferred embodiment, the spacers 240 are circumferentially andevenly spaced about the first outer surface 146 of the holder assembly110. The spacers 240 are preferably formed of a soft wearable material,such as Teflon, which prevents scoring of the gland inner surface duringrotational movement of the holder assembly 110. Although the FIG. 18embodiment shows four evenly separated spacers, any number and spacingof spacers can be employed. Additionally, the spacers 240 need not beformed on the holder first outer surface 146, but can be formed atvarious holder locations.

Other suitable centering mechanism may also be used.

When the gland assembly 40 and the holder assembly 110 are properlyaligned, the gland gasket 76 and the holder gasket 160 are captured inseparate gasket grooves formed on opposite sealing faces of the glandand holder segments. This double-capture configuration allows themechanical seal 10 to withstand higher pressures without degradation ofthe pressure and fluid seals formed at the segment sealing faces.Additionally, the O-ring 202 forms a pressure-tight and fluid-tight sealbetween the gland inner surface, e.g. gland second face 50 and firstwall 48, and the outer surface 36 of the stationary seal ring 30.

After the mechanical seal is assembled and mounted to the pump housing14, the pump process medium, e.g. hydraulic fluid, is sealed within aprocess medium channel 234, as shown in FIG. 3, defined by the glandinner surface 54 (excluding the gland first face 46), O-ring 202, theholder assembly outer surface 116, the stationary seal ring outersurface 190 and abutment 192, the rotary seal ring first and secondsurfaces 180,182, the holder assembly inner surface 124, and O-ring 188.The ambient environment medium, typically air, fills an ambient processchannel 236, typically sealed from the process channel 234, that isdefined by the stationary and rotary seal ring inner surfaces 35, 172,the stationary ring outer surface 190, the gland first and second faces46, 50 and first wall 48, the rotary seal ring third outer surface 184,and the holder assembly first wall 132. The phrase “ambient environment”is intended to include any external environment other than the internalenvironment of the housing 14.

The stationary and rotary seal ring segment sealing faces 22, 32 areplaced in sealing contact with the other segment of the pair by theradial force of the O-rings 188 and 202. In addition, the hydraulicpressure of the process medium contained within the process channel 234exerts an additional radially inward force, proportional to the fluidpressure, upon the seal ring segment outer surfaces 36,190, biasing thesegment sealing faces 32 together.

Overall, the O-ring 142 prevents the seepage of process medium along theshaft 12 and into the ambient process channel 236. The flat gasket 60prevents the seepage of process medium along the housing 14 andmechanical seal 10 interface and the O-rings 188 and 202 prevent processmedium from invading the ambient process channel 236 by way of theholder assembly 110 and the gland 40, respectively.

The illustrative mechanical seal assembly of the illustrativeembodiments of the invention provide significant advantages over theprior art, including ease of installation of the mechanical sealassembly and functional improvements. For example, the use of the detentgroove and/or the double-angled lead-in on the holder assembly innersurface enables improved rotary face insertion, with less insertionforce required. The insertion force may be reduced by between about 59%and 70%, though the invention is not limited to this range. By loweringthe insertion force, the installer is less likely to damage the sealfaces upon installation, thereby prolonging the lifetime of the sealcomponents and improving overall operation. The illustrativeconfiguration may also eliminate the need to hold the rotary seal facein position during installation, because the detent groove automaticallypositions the rotary seal face in a proper position. During operation,the detent groove provides improved squaring of the rotary seal facerelative to the shaft, and prevents the rotary seal ring and/orassociated O-ring from moving and/or popping out of position, which canbe difficult to fix. The double-angled lead-in also allows the holder tobe first tightened to the shaft before insertion of the rotary seal ringand O-ring, which results in improved squaring of the rotary seal facerelative to the shaft.

In addition, the overlapping gland segments prevent sliding of the glandsegments relative to each other when force is applied to the assembly,thereby improving performance and extending the lifetime of the sealcomponents.

It will thus be seen that the invention efficiently attains the objectsset forth above, among those made apparent from the precedingdescription. Since certain changes may be made in the aboveconstructions without departing from the scope of the invention, it isintended that all matter contained in the above description or shown inthe accompanying drawings be interpreted as illustrative and not in alimiting sense.

It is also to be understood that the following claims are to cover allgeneric and specific features of the invention described herein, and allstatements of the scope of the invention which, as a matter of language,might be said to fall therebetween.

1. A gland assembly of a split mechanical seal assembly for providing aseal around a shaft, the shaft extending along a longitudinal axis fromstationary equipment, the gland assembly comprising: a first arcuategland segment having a first interfacing surface formed at a first endand a second interfacing surface formed at a second end; and a secondarcuate gland segment having a third interfacing surface formed at afirst end configured to couple to the first interfacing surface, and afourth interfacing surface at a second end configured to couple to thesecond interfacing surface to form an annular gland assembly, wherein atleast one pair of the coupled interfacing surfaces are non-flat andshaped complimentary to each other to transmit a bolting force to theother mating gland segment.
 2. The gland assembly of claim 1, whereinthe first interfacing surface includes a protrusion and the thirdinterfacing surface includes a recess sized and configured to receivethe protrusion to secure the first arcuate gland segment to the secondarcuate gland segment.
 3. The gland assembly of claim 1, wherein thefirst interfacing surface is a stepped surface having a first flat,axially-extending face, a second flat, axially-extending face and afirst radially-extending face connecting the first and second flat,axially-extending faces.
 4. The gland assembly of claim 3, wherein theaxially-extending faces are parallel to each other, and theradially-extending face extends perpendicular to the axially-extendingfaces.
 5. The gland assembly of claim 3, wherein the second interfacingsurface is a stepped surface having a third flat, axially-extendingface, a fourth flat, axially-extending face and a second-radiallyextending face connecting the third and fourth flat, axially-extendingfaces.
 6. The gland assembly of claim 4, wherein the first and secondradially-extending faces abut each other when the gland assembly isassembled to form an overlap.
 7. The gland assembly of claim 2, whereinthe first interfacing surface further includes a recess and the thirdinterfacing surface includes a protrusion sized and dimensioned to bereceived by the recess.
 8. The gland assembly of claim 2, wherein thesecond interfacing surface includes a protrusion and the fourthinterfacing surface includes a recess sized and configured to receivethe protrusion to secure the second end of the first arcuate glandsegment to the second end of the second arcuate gland segment.
 9. Thegland assembly of claim 8, wherein the second interfacing surfacefurther includes a recess and the fourth interfacing surface includes aprotrusion sized and dimensioned to be received by the recess in thesecond interfacing surface.
 10. A split mechanical seal assembly,comprising: a pair of stationary gland segments defining a chamber andhaving an inner face, each gland segment having at least one interfacingsurface configured to interface with and overlap a correspondinginterfacing surface of the other gland segment; a pair of rotatingholder segments disposed within said chamber and radially spaced fromsaid gland segments; a stationary seal ring assembly disposed withinsaid chamber and axially spaced from said holder segments; and arotating seal ring assembly disposed within said rotating holder andaxially spaced from and in intimate contact with said stationary sealring.
 11. The split mechanical seal assembly of claim 10, wherein afirst interfacing surface on a first gland segment includes a protrusionand a corresponding interfacing surface includes a recess sized andconfigured to receive the protrusion to secure the first gland segmentto the second gland segment.
 12. The split mechanical seal assembly ofclaim 10, wherein the first interfacing surface is a stepped surfacehaving a first flat, axially-extending face, a second flat,axially-extending face and a first radially-extending face connectingthe first and second flat, axially-extending faces.
 13. The splitmechanical seal assembly of claim 12, wherein the axially-extendingfaces are parallel to each other, and the radially-extending faceextends perpendicular to the axially-extending faces.
 14. The splitmechanical seal assembly of claim 12, wherein the correspondinginterfacing surface is a stepped surface having a third flat,axially-extending face, a fourth flat, axially-extending face and asecond-radially extending face connecting the third and fourth flat,axially-extending faces.
 15. The split mechanical seal assembly of claim14, wherein the first and second radially-extending faces abut and lieflat against each other when the gland assembly is assembled to form anoverlap.
 16. The split mechanical seal assembly of claim 10, wherein theholder has a detent groove that is curved in two dimensions and formedon a radially inner surface of the holder, the detent groove configuredto receive and retain a radially-outer portion of an O-ring disposedabout the rotating seal ring assembly.
 17. The split mechanical sealassembly of claim 10, wherein the holder has a radially inner surfacehaving a first sloped face extending radially and axially inward from anaxially forward end of the holder, wherein the first sloped face extendsat a first angle relative to a longitudinal axis of the mechanical sealassembly.
 18. The split mechanical seal assembly of claim 17, whereinthe radially inner surface of the holder has a second sloped faceextending radially and axially inward from the first sloped face, thesecond sloped face extending at a second angle relative to alongitudinal axis of the mechanical seal assembly.
 19. The splitmechanical seal assembly of claim 18, further comprising a detent grooveformed on the second sloped face, the detent groove sized and configuredto receive and retain a radially-outer portion of an O-ring disposedabout the rotating seal ring assembly.
 20. A method of assembling agland for a split mechanical seal assembly, comprising the steps of:providing a first arcuate gland segment having a first interfacingsurface formed at a first end a second interfacing surface formed at asecond end, wherein the first interfacing surface is non-flat; providinga second arcuate gland segment having a third interfacing surface formedat a first end configured to couple to the first interfacing surface anda fourth interfacing surface at a second end, wherein the thirdinterfacing surface is non-flat and shaped complimentary to the firstinterfacing surface; and coupling the first interfacing surface and thethird interfacing surface, and the second interfacing surface to thefourth interfacing surface to form an annular gland assembly, such thata portion of the first interfacing surface overlaps a portion of thesecond interfacing surface to transmit a bolting force to from onesegment to the other.
 21. The method of claim 20, wherein the firstinterfacing surface includes a protrusion and the third interfacingsurface includes a recess sized and configured to receive the protrusionto secure the first arcuate gland segment to the second arcuate glandsegment.
 22. The method of claim 20, wherein the first interfacingsurface is a stepped surface having a first flat, axially-extendingface, a second flat, axially-extending face and a firstradially-extending face connecting the first and second flat,axially-extending faces.
 23. The method of claim 22, wherein theaxially-extending faces are parallel to each other, and theradially-extending face extends perpendicular to the axially-extendingfaces.
 24. The method of claim 22, wherein the second interfacingsurface is a stepped surface having a third flat, axially-extendingface, a fourth flat, axially-extending face and a second-radiallyextending face connecting the third and fourth flat, axially-extendingfaces.
 25. The gland assembly of claim 24, wherein the first and secondradially-extending faces abut and lie flat against each other when thegland assembly is assembled to form an overlap.